EP3299622B1 - Elektrische pumpe - Google Patents

Elektrische pumpe Download PDF

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Publication number
EP3299622B1
EP3299622B1 EP16796219.0A EP16796219A EP3299622B1 EP 3299622 B1 EP3299622 B1 EP 3299622B1 EP 16796219 A EP16796219 A EP 16796219A EP 3299622 B1 EP3299622 B1 EP 3299622B1
Authority
EP
European Patent Office
Prior art keywords
rotor
shaft
assembled
pump
motor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP16796219.0A
Other languages
English (en)
French (fr)
Other versions
EP3299622A4 (de
EP3299622A1 (de
Inventor
Donghui Wang
Hiroaki Usui
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Shinano Kenshi Co Ltd
Original Assignee
Shinano Kenshi Co Ltd
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Publication date
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Publication of EP3299622A1 publication Critical patent/EP3299622A1/de
Publication of EP3299622A4 publication Critical patent/EP3299622A4/de
Application granted granted Critical
Publication of EP3299622B1 publication Critical patent/EP3299622B1/de
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Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/04—Pumps having electric drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/001—Noise damping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/06—Means for converting reciprocating motion into rotary motion or vice versa
    • H02K7/075—Means for converting reciprocating motion into rotary motion or vice versa using crankshafts or eccentrics
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with bearings
    • H02K7/083—Structural association with bearings radially supporting the rotary shaft at both ends of the rotor
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/14—Structural association with mechanical loads, e.g. with hand-held machine tools or fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0044—Pulsation and noise damping means with vibration damping supports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B45/00—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
    • F04B45/04—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having plate-like flexible members, e.g. diaphragms
    • F04B45/047—Pumps having electric drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/22—Arrangements for enabling ready assembly or disassembly
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/04—Balancing means

Definitions

  • the present invention relates to an electric pump which drives a pump by a motor used for, for example, OA equipment, home electric appliances, industrial equipment, medical equipment and so on.
  • a motor includes a rotor and a stator in a motor casing, a rotor shaft extended from the motor casing to a pump-body side and a motor driving circuit substrate.
  • One ends of a pair of connecting rods are respectively assembled to the rotor shaft extended to the pump-body side through a pair of bearings.
  • the pair of connecting rods are respectively assembled to positions where phases are shifted by 180 degrees.
  • the other ends of the pair of connecting rods are respectively coupled to diaphragms through retainers.
  • the diaphragm, a valve seat and a pump head portion are assembled to the pump body.
  • a cylindrical eccentric shaft for cancelling the eccentricity of the pair of connecting rods is assembled to the vicinity of a shaft end of the rotor shaft extended on the pump-body side, and the connecting rods are assembled to the eccentric shaft through the bearings.
  • DE102013003513A1 discloses a compressor arrangement for operating a compressed air supply system of a vehicle, comprising a compressor comprising: an electric motor formed as an electronically commutated, brushless DC motor with a drive circuit comprising power electronics, and a pneumatic compressor.
  • the electric motor is formed in the form of an external rotor motor.
  • the electric pump disclosed in Patent Literature 1 is an outer-rotor type motor in which the rotor of the motor is formed in a cup shape, which is assembled so that a top surface portion of a rotor yoke is directed to the shaft end, in which both ends of the rotor shaft are rotatably supported by a pair of bearings provided in the motor casing on both sides of the rotor yoke in the axial direction.
  • the shaft length of the rotor shaft becomes long and a distance from the bearing (fulcrum) on the motor side to the connecting rod (point of action) becomes long, therefore, the device is increased in size and the rotor shaft tends to vibrate, which will be a factor of noise.
  • the connecting rods are assembled to the eccentric shaft through the bearings after the cylindrical eccentric shaft is assembled to the rotor shaft extended on the pump body side, therefore, backlash or vibration tends to occur due to shaft misalignment between many assembling parts such as the rotation shaft, the eccentric shaft, the bearings and the connecting rods.
  • the present invention has been accomplished under the circumstances in view. It is an object thereof to provide an electric pump capable of reducing the device size in the axial direction with low vibration and low noise as well as with high rotational stability.
  • the present invention has the following structure in order to achieve the above object.
  • the rotor is integrally assembled to the rotor shaft in the state where the opening of the rotor formed in a cup shape is directed to the shaft end on the motor side, therefore, the intermediate bearing can be arranged closely to the top surface portion of the rotor by using a free space inside the opening of the rotor.
  • the distance from the intermediate bearing to the eccentric cam to which the crank shaft is connected can be reduced as short as possible, thereby suppressing occurrence of vibration and noise as well as reducing the device size in the axial direction by shortening the shaft length of the rotor shaft.
  • the intermediate bearing having a relatively larger diameter is used in an opening of a rotor yoke, thereby improving the rotational stability of the rotor.
  • the eccentric cam is integrally provided with a balance weight portion for cancelling the eccentricity of the crank shaft assembled through the cam bearing.
  • the rotor yoke, the eccentric cam and the balance weight portion are integrally formed, therefore, shaft alignment between components are performed and the eccentricity is cancelled, thereby reducing vibration, the number of components and assembly man hours to improve assembling property.
  • a shaft end of the rotor shaft of the motor extended from the eccentric cam to the crank mechanism side is rotatably supported by a crank side bearing assembled to the case body.
  • the shaft end of the rotor shaft on the crank-mechanism side on which an external force acts is rotatably supported by the crank-side bearing assembled to the case body, thereby suppressing the runout of the rotor shaft.
  • the crank side bearing when the crank side bearing is assembled to the case body through an elastic body, the amount of shaft misalignment between the rotor shaft and the crank-side bearing can be absorbed by deformation of the elastic body as well as vibration at the shaft end of the rotor shaft can be reduced.
  • the intermediate bearing When the intermediate bearing is assembled inside the opening of the rotor closely to the top surface portion of the rotor, the distance between the crank shaft connecting to the eccentric cam and the intermediate bearing can be reduced as short as possible, therefore, vibration of the crank shaft reciprocating by the rotatory drive of the motor is suppressed and occurrence of noise is also suppressed.
  • the intermediate bearing may be formed by plural bearings assembled closely in the axial direction. According to the structure, the rotational stability of the rotor is improved even when small bearings are used.
  • the rotor is formed so that a rotor hub assembled to block an end surface of the rotor yoke formed in a cylindrical shape is integrally assembled to the rotor shaft, and that the rotor is rotatably supported through the intermediate bearing assembled between the rotor hub and a stator housing.
  • the rotor yoke and the rotor hub which form the rotor can be separately manufactured, thereby easily forming the rotor hub and the eccentric cam integrally with shaft alignment.
  • the assembly between the rotor and the rotor yoke as well as the assembly between the rotor hub and the eccentric cam can be easily performed.
  • the rotor is rotatably supported through the intermediate bearing assembled between the stator housing and the rotor hub, therefore, the intermediate bearing provided in the opening of the rotor can be arranged as closely as possible to the eccentric cam, which can reduce the distance between a fulcrum and a point of action and can improve the rotational stability of the rotor.
  • the electric pump may be a diaphragm pump in which the other end of the crank shaft is coupled to a diaphragm facing a pump chamber. Accordingly, a small-sized electric diaphragm pump with less vibration can be provided.
  • an electric pump P has a motor and a crank mechanism driven by the motor are integrally assembled inside a case body 2 which is adjacent to a pump case 1.
  • An outer-rotor type DC brushless motor 3 is used as an example of the motor, and a diaphragm pump 4 is used as an example of the pump.
  • Other pumps such as a piston pump provided with a cylinder and a piston in the case body 2 may be adopted instead of using the diaphragm pump 4.
  • the outer-rotor type DC brushless motor 3 includes a stator 5 and a rotor 6.
  • a motor substrate 8 and a stator core 9 are respectively assembled to a cylindrical stator housing 7 which is fixed to the case body 2.
  • the motor substrate 8 is assembled so as to overlap a flange portion 7a formed in the stator housing 7.
  • the motor substrate 8 is provided with a sensor substrate on which hall devices and so on are mounted, power feeding terminals to a motor coil and so on.
  • a flexible cable 8a connecting to the motor substrate 8 is drawn out from the case body 2 (see Fig. 1, Fig. 2 ).
  • the not-shown motor coil is wound around pole teeth 9a which are radially formed in the stator core 9.
  • the rotor 6 is formed in a cup shape one end in the axial direction of which opens.
  • a rotor shaft 10 is integrally assembled to a rotor hub 6b which is assembled to block one end surface of a rotor yoke 6a formed in a cylindrical shape. That is, the rotor 6 is integrally assembled so that an opening of the rotor yoke 6a is directed to a shaft end on the motor side and the rotor shaft 10 is pressed into the rotor hub 6b provided on a top surface portion.
  • An annular magnet 6c is provided on an inner peripheral surface of the rotor yoke 6a. The magnet 6c is assembled at a position facing the pole teeth 9a of the stator core 9.
  • An eccentric cam 6d is integrally formed in the rotor hub 6b.
  • a balance weight 6e (counter weight) is further formed in the eccentric cam 6d. This is provided for cancelling the eccentricity of a crank shaft 12 one end of which is assembled to the eccentric cam 6d through a cam bearing 11.
  • the rotor 6 may use the rotor yoke 6a integrally molded in a cup shape by drawing a metal magnetic substance (for example, a galvanized steel sheet), and the eccentric cam 6d may be integrally assembled to a top surface portion of the rotor yoke 6a.
  • a metal magnetic substance for example, a galvanized steel sheet
  • An intermediate bearing 13 is assembled between the stator housing 7 and the rotor hub 6b. That is, the intermediate bearing 13 is provided inside the opening of the rotor 6 closely to the top surface portion (rotor hub 6b).
  • the intermediate bearing 13 rotatably supports the rotor 6. Accordingly, a distance from the intermediate bearing 13 to the eccentric cam 6d to which the crank shaft 12 is connected can be reduced as short as possible, thereby suppressing occurrence of vibration and noise as well as reducing the device size in the axial direction by shortening the shaft length of the rotor shaft 10. Furthermore, as the intermediate bearing 13 is provided inside the opening of the rotor 6 (rotor hub 6b), the rotational stability of the rotor 6 is improved. As for the intermediate bearing 13, plural bearings may be assembled closely in the axial direction.
  • the rotor shaft 10 is rotatably supported by a motor-side bearing 14 one end of which is assembled to an end portion the stator housing 7.
  • the motor-side bearing 14 is assembled to the stator housing 7 by being preloaded toward the outer side in the axial direction while falling-off is prevented by an E-ring and so on.
  • the rotor shaft 10 is inserted through the stator housing 7, and the other end side is extended to the crank mechanism side of the case body 1.
  • the other end of the rotor shaft 10 is rotatably supported by a crank-side bearing 15 assembled to the case body 1.
  • the rotor shaft 10 is assembled to the case body 1 while falling-off is prevented by an E-ring and so on.
  • the crank-side bearing 15 is assembled to the case body 1 through an elastic body 16 (an O-ring, an annular rubber and so on).
  • the shaft end of the rotor shaft 10 on the crank-mechanism side on which an external force acts is rotatably supported by the crank-side bearing 15, thereby suppressing the runout of the rotor shaft 10.
  • the crank-side bearing 15 is assembled to the case body 1 through the elastic body 16, the amount of shaft misalignment between the rotor shaft 10 and the crank-side bearing 15 can be absorbed by deformation of the elastic body 16 as well as vibration at the shaft end of the rotor shaft 10 can be reduced.
  • the cam bearing 11 is assembled to an outer periphery of the eccentric cam 6d which is integrally assembled to the top surface portion (rotor hub 6b) of the rotor 6.
  • One end of the crank shaft 12 is assembled through the cam bearing 11.
  • the other end of the crank shaft 12 is coupled to a diaphragm 17 facing a pump chamber 18 on the diaphragm pump 4 side.
  • the diaphragm 17 is assembled in a state of being sandwiched between the case body 2 and the pump case 1 in which the pump chamber 18 is formed.
  • a pump head 19 is integrally assembled to the pump case 1 through a sealing material 20.
  • the pump head 19 is fixed to the pump case 1 by bolts 21 at four corners.
  • a suction port 19a and a discharge port 19b of fluid are formed in the pump head 19.
  • a suction passage 19c communicating with the suction port 19a is formed in the pump head 19.
  • a suction port 1a communicating with the suction passage 19c is formed in the pump case 1.
  • the suction passage 1a communicates with the pump chamber 18.
  • a suction-side check valve 22a is provided at an interface between the pump head 19 and the pump case 1.
  • the suction-side check valve 22a is provided at a position where the suction passage 19a and the suction passage 1a which communicates with the suction passage 19a are partitioned.
  • the suction-side check valve 22a opens when a fluid pressure inside the pump chamber 18 is negative, and closes when the fluid pressure is balanced or positive.
  • a discharge passage 19d communicating with the discharge port 19b is formed in the pump head 19.
  • a discharge passage 1b communicating with the discharge passage 19d is formed in the pump head 19.
  • the discharge passage 1b communicates with the pump chamber 18.
  • a discharge-side check valve 22b is provided at an interface between the pump head 19 and the pump case 1.
  • the discharge-side check valve 22b is provided at a position where the discharge passage 19b and the discharge passage 1b communicating with the discharge passage 19b are partitioned.
  • the discharge-side check valve 22b opens when the fluid pressure inside the pump chamber 18 is positive and closed when the fluid pressure is balanced or negative.
  • the motor (the outer-rotor type DC brushless motor 3) is driven to be rotated, thereby converting the rotary motion of the eccentric cam 6d around the rotary shaft 10 into the reciprocating motion of the crank shaft 12 and deforming the diaphragm 17 to repeat operations of discharging the fluid inside the pump chamber 18 from the discharge port 19b and sucking the fluid from the suction port 19a.
  • the rotor 6 formed in the cup shape is integrally assembled to the rotor shaft 10 with the opening being directed toward the shaft end of the motor side, therefore, the intermediate bearing 13 can be arranged closely to the top surface portion of the rotor 6 by using a free space inside the opening of the rotor 6.
  • the distance from the intermediate bearing 13 to the eccentric cam 6d to which the crank shaft 12 is connected can be reduced as short as possible, thereby suppressing occurrence of vibration and noise as well as reducing the device size in the axial direction by shortening the shaft length of the rotor shaft 10.
  • the intermediate bearing 13 having a relatively large diameter is used in the opening of the rotor 6, the rotational stability of the rotor 6 is improved.
  • the eccentric cam 6d and the balance weight 6e are integrally provided, shaft alignment between components is made and the eccentricity is cancelled, thereby reducing the number of components and reducing assembly man hours as well as reducing vibration and improving the rotational stability of the rotor 6.
  • the shaft end of the rotor shaft 10 on the crank-mechanism side on which the external force acts is rotatably supported by the crank-side bearing 15, thereby suppressing the runout of the rotor shaft 10.
  • the crank-side bearing 15 is assembled to the case body 1 through the elastic body 16, the amount of shaft misalignment between the rotor shaft 10 and the crank-side bearing 15 can be absorbed by deformation of the elastic body 16 as well as vibration at the shaft end of the rotor shaft 10 can be reduced.
  • the distance from the crank shaft 12 connecting to the eccentric cam 6d to the intermediate bearing 13 can be reduced as short as possible, therefore, vibration of the crank shaft 12 reciprocating by the rotary drive of the motor is suppressed and the occurrence of noise can be also suppressed.
  • crank shaft 12 is connected to the rotor shaft 10 at one place (the pump chamber 18 exists at one place) in the electric pump P has been explained, however, it is also preferable that the crank shaft 12 is connected to the rotor shaft 10 at plural places and plural pump chambers 18 are provided.
  • crank shafts 12 are respectively provided in the rotor shaft 10 at positions phases of which are displaced by 180 degrees through cam bearings 11 and that a pair of balance weights 6e are respectively provided in the eccentric cam 6d at positions phases of which are displaced by 180 degrees with respect to the crank shafts 12, thereby achieving counterbalance.
  • the crank mechanisms may be provided on both sides of the motor and plural diaphragm pumps 4 may be provided.
  • the pump cases 1 and the pump heads 19 are provided in the casing 2 at two places.
  • the suction ports 19a and the discharge ports 19b are provided at positions inverted by 180 degrees in the right and left pair of diaphragm pumps 4.
  • a basic structure (the left side of Fig. 8 ) of the electric pump (the outer-rotor type DC brushless motor 3 and the diaphragm pump 4) is similar to that of Fig. 3 , therefore, a different structure (an expanded portion on the right side of Fig. 8 ) will be mainly explained.
  • the same numerals are given to the same members as those of Fig. 3 and explanation will be invoked.
  • the rotor shaft 10 is extended by the motor-side bearing 14 of the outer-rotor type DC brushless motor 3 and the shaft end thereof is rotatably supported by an expansion-side bearing 23 of the case body 1.
  • the rotor shaft 10 is assembled to the case body 1 while falling-off is prevented by an E-ring and so on.
  • the expansion-side bearing 23 is preferably assembled to the case body 1 through the elastic body 16 (the O-ring, the annular rubber and so on).
  • An expansion-side eccentric cam 24 is integrally assembled to the rotor shaft 10 extended to the motor side.
  • a balance weight 24a (counter weight) is integrally formed in the expansion-side eccentric cam 24. This is provided for cancelling the eccentricity of the expansion-side crank shaft 12 on end side of which is assembled to the expansion-side eccentric cam 24 through the cam bearing 11. It is preferable that the expansion-side eccentric cam 24 is arranged as closely as possible to the motor-side bearing 14.
  • the rotation of the rotor 6 of the same DC brushless motor 3 can be converted into the reciprocating motion of the two crank shaft 12 connecting to the rotor shaft 10 to thereby drive two diaphragm pumps 4 at the same time.
  • a pair (two cylinders) of piston pumps or two pairs (four cylinders) of piston pumps in which cylinders and pistons are provided in the case body 2 may be provided instead of the diaphragm pumps 4.
  • the above electric pump P is used to a wide range of apparatuses such as OA equipment, home electric appliances, industrial equipment, medical equipment and so on.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Reciprocating Pumps (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Claims (8)

  1. Elektrische Pumpe (P), in der ein Motor (3) und ein vom Motor (3) angetriebener Kurbelmechanismus in einem Gehäusekörper (2) benachbart zu einer Pumpe (4) einstückig montiert sind, umfassend:
    einen Rotor (6), der in einer Becherform ausgebildet ist und der einstückig an einer Rotorwelle (10) angebracht ist, die sich von der Motor(3)-Seite zur Kurbelmechanismusseite innerhalb des Gehäusekörpers (2) erstreckt, in einem Zustand, in dem eine Öffnung des Rotors (6) zu einem Wellenende auf der Motor(3)-Seite gerichtet ist und der Rotor (6) von einem Zwischenlager (13), das innerhalb der Öffnung angebracht ist, drehbar gelagert ist;
    einen Exzenternocken (6d), der einstückig mit einem oberen Oberflächenabschnitt des Rotors (6) bereitgestellt ist, der exzentrisch zu einem Wellenmittelpunkt der Rotorwelle (10) vorliegt; und
    eine Kurbelwelle (12), deren eine Endseite über ein Nockenlager (11) an dem Exzenternocken (6d) angebracht ist und deren andere Endseite mit der Pumpen (4)-Seite verbunden ist;
    wobei der Motor (3) zum Drehen angetrieben wird, wodurch eine Drehbewegung des Exzenternockens (6d) um die Rotorwelle (10) in eine Hin- und Herbewegung der Kurbelwelle (12) umgewandelt und die Pumpe (4) angetrieben wird.
  2. Elektrische Pumpe (P) nach Anspruch 1,
    wobei der Exzenternocken (6d) einstückig mit einem Ausgleichsgewicht (6e) zum Aufheben der Exzentrizität der durch das Nockenlager (11) angebrachten Kurbelwelle (12) in Bezug auf den Wellenmittelpunkt der Rotorwelle (10) bereitgestellt ist.
  3. Elektrische Pumpe (P) nach Anspruch 1 oder 2,
    wobei ein Wellenende der Rotorwelle (10) des Motors (3), das sich vom Exzenternocken (6d) zur Kurbelmechanismusseite erstreckt, drehbar von einem kurbelseitigen Lager (15) gelagert wird, das an dem Gehäusekörper (2) angebracht ist.
  4. Elektrische Pumpe (P) nach Anspruch 3,
    wobei das kurbelseitige Lager (15) durch einen elastischen Körper (16) an dem Gehäusekörper (2) angebracht ist.
  5. Elektrische Pumpe (P) nach einem der Ansprüche 1 bis 4,
    wobei das Zwischenlager (13) innerhalb der Öffnung des Rotors (6) eng an dem oberen Oberflächenabschnitt des Rotors (6) angebracht ist.
  6. Elektrische Pumpe (P) nach Anspruch 5,
    wobei das Zwischenlager (13) durch mehrere Lager gebildet ist, die in axialer Richtung eng aneinander angebracht sind.
  7. Elektrische Pumpe (P) nach einem der Ansprüche 1 bis 6,
    wobei der Rotor (6) so ausgebildet ist, dass eine Rotornabe (6b), die zum Blockieren einer Endfläche eines in einer zylindrischen Form ausgebildeten Rotorjochs (6a) angebracht ist, einstückig an der Rotorwelle (10) angebracht ist, und
    der Rotor (6) durch das Zwischenlager (13), das zwischen der Rotornabe (6b) und einem Statorgehäuse (7) montiert ist, drehbar gelagert ist.
  8. Elektrische Pumpe (P) nach einem der Ansprüche 1 bis 7,
    wobei die elektrische Pumpe (P) eine Membranpumpe (4) ist, in der das andere Ende der Kurbelwelle (12) mit einer Membran gekoppelt ist, die einer Pumpenkammer (18) zugewandt ist.
EP16796219.0A 2015-05-18 2016-04-08 Elektrische pumpe Active EP3299622B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015101054A JP6074456B2 (ja) 2015-05-18 2015-05-18 電動ポンプ
PCT/JP2016/061482 WO2016185825A1 (ja) 2015-05-18 2016-04-08 電動ポンプ

Publications (3)

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EP3299622A1 EP3299622A1 (de) 2018-03-28
EP3299622A4 EP3299622A4 (de) 2019-01-23
EP3299622B1 true EP3299622B1 (de) 2020-12-02

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EP16796219.0A Active EP3299622B1 (de) 2015-05-18 2016-04-08 Elektrische pumpe

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US (1) US10323631B2 (de)
EP (1) EP3299622B1 (de)
JP (1) JP6074456B2 (de)
CN (1) CN106795872B (de)
WO (1) WO2016185825A1 (de)

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US10584694B2 (en) * 2016-02-09 2020-03-10 Oridion Medical 1987 Ltd. Miniature diaphragm pump with enlarged operation time
US10760566B2 (en) * 2016-07-22 2020-09-01 Nocira, Llc Magnetically driven pressure generator
EP3585335B1 (de) 2017-02-27 2024-05-08 Nocira, LLC Ohrpumpen
JP2019012105A (ja) * 2017-06-29 2019-01-24 日本電産株式会社 ケーシングユニット
US10619706B2 (en) * 2017-08-21 2020-04-14 Shinano Kenshi Kabushiki Kaisha Speed reducer and motor with speed reducer
CN107882723A (zh) * 2017-10-11 2018-04-06 中国航发西安动力控制科技有限公司 一种微型隔膜泵
CN209145818U (zh) * 2018-09-28 2019-07-23 深圳华星恒泰泵阀有限公司 一种带流量计的微型隔膜水泵
WO2021202663A1 (en) * 2020-03-31 2021-10-07 Graco Minnesota Inc. Pump drive system
AU2021248838A1 (en) * 2020-03-31 2022-10-13 Graco Minnesota Inc. Pump drive system
AU2021246059A1 (en) 2020-03-31 2022-10-06 Graco Minnesota Inc. Electrically operated displacement pump
KR102344890B1 (ko) * 2020-10-15 2021-12-29 엘지전자 주식회사 왕복동식 압축기
CN114649917B (zh) 2022-05-19 2022-08-05 浙大城市学院 一种二维电机组合活塞泵

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JP2000297744A (ja) * 1999-04-16 2000-10-24 Erc:Kk 電動ポンプ
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JP2007239737A (ja) * 2006-02-13 2007-09-20 Nidec Sankyo Corp ミキシングポンプ装置および燃料電池
DE102008005820A1 (de) * 2007-09-11 2009-03-12 Continental Teves Ag & Co. Ohg Motor-Pumpenaggregat
JP5559070B2 (ja) * 2011-01-25 2014-07-23 株式会社ケーヒン 燃料電池用エゼクタ装置
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Also Published As

Publication number Publication date
US20180106244A1 (en) 2018-04-19
EP3299622A4 (de) 2019-01-23
EP3299622A1 (de) 2018-03-28
CN106795872B (zh) 2018-10-12
CN106795872A (zh) 2017-05-31
JP2016217212A (ja) 2016-12-22
US10323631B2 (en) 2019-06-18
JP6074456B2 (ja) 2017-02-01
WO2016185825A1 (ja) 2016-11-24

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